CN112033672B - Calibration device and calibration method for static and dynamic load identification of ship radial bearing - Google Patents
Calibration device and calibration method for static and dynamic load identification of ship radial bearing Download PDFInfo
- Publication number
- CN112033672B CN112033672B CN202010928382.XA CN202010928382A CN112033672B CN 112033672 B CN112033672 B CN 112033672B CN 202010928382 A CN202010928382 A CN 202010928382A CN 112033672 B CN112033672 B CN 112033672B
- Authority
- CN
- China
- Prior art keywords
- loading
- bearing
- calibration
- strain
- test
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
Images
Classifications
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M13/00—Testing of machine parts
- G01M13/04—Bearings
Landscapes
- Physics & Mathematics (AREA)
- General Physics & Mathematics (AREA)
- Force Measurement Appropriate To Specific Purposes (AREA)
- Testing Of Devices, Machine Parts, Or Other Structures Thereof (AREA)
Abstract
The invention discloses a calibration device and a calibration method for identifying static and dynamic loads of a ship radial bearing, which comprise the following steps: the device comprises a wireless remote measuring device, a key phase signal acquisition device, a balance weight disc, a strain gauge, a loading device and a pressure sensor, wherein the loading device can select an axial loading mode, a radial loading mode or a mixed loading mode for a test bearing, and select three working conditions of simulating unbalanced force, impact force and sine excitation, so that the device has abundant static and dynamic calibration conditions, and can simulate the external influence born by the bearing in the service period of a ship more truly. The invention provides a calibration method for calculating a test system error and an identification model error in test data analysis.
Description
Technical Field
The invention relates to a calibration device and a calibration method for identifying static and dynamic loads of a radial bearing of a ship, in particular to identification and calibration of dynamic loads borne by a bearing of a ship propulsion shafting in a service period.
Background
At present, with the rapid development of the shipping industry, the development trend of large-scale ships is increasingly prominent. In order to meet the requirement of larger torque transmission, the diameters of a ship propulsion shafting and a propeller are continuously increased, so that the rated load value of the shafting design is correspondingly increased, but a plurality of uncertain factors can cause unbalanced load distribution of bearings in the propulsion shafting in the actual service period of a ship, serious potential safety hazards are caused to the ship propulsion shafting, and identification of the load of the bearings of the ship propulsion shafting in the service period is a development trend for manufacturing the future ship propulsion shafting. In recent years, more and more researchers calculate the bearing load by measuring the section strain of the shafting, the method is simple and convenient to operate and small in calculated amount, but the identification precision is poor due to the change of external conditions in the service period of the ship and the like. Therefore, the calibration in the process of identifying the static and dynamic loads of the radial bearing of the ship is a key technology for improving the identification precision of the loads of the bearing.
Aiming at the problem of improving the identification precision of static and dynamic loads of a radial bearing of a ship, a precision increasing method for calculating errors of a test system and errors of an identification model in test data analysis is provided. The reason for this is that: when the ship radial bearing is subjected to external condition changes in the actual service period, the position of the equivalent fulcrum of the bearing changes, and the identification model defaults the equivalent fulcrum of the bearing to be the midpoint of the bearing, so that the test precision is influenced; the bearing load obtained by the test system has obvious errors due to the influence of surrounding noise and other factors in the process of transmitting the strain signal, so that the errors of the test system and the errors of the identification model must be included in the analysis of the test result. The position of the equivalent fulcrum and the strain correction range are determined by calibrating the static and dynamic load of the radial bearing of the ship, and a foundation is laid for monitoring the load of the bearing of the ship in real time in service. In a traditional ship radial bearing calibration device, under a static or quasi-static condition, the influence of external factors on a bearing load identification value is simulated by changing the elevation of a bearing, adding a mass block on a wheel disc and applying a load by using hydraulic jacking equipment, and a simulation test is not carried out on uncertain factors such as impact force generated by wave slapping or loading condition change in the service period of a ship propulsion shaft system, hydrodynamic force of a propeller, gas force and inertia force generated by combustion of a diesel engine and the like.
Disclosure of Invention
Aiming at the defects or the improvement requirements in the prior art, the invention provides the calibration device and the calibration method for identifying the static and dynamic loads of the radial bearing of the ship, which have the advantages of high precision, simplicity in operation, short calculation time, rich simulated working conditions and the like, and are particularly suitable for calibrating the load identification method of the radial bearing of the ship propulsion shafting in the service period.
To achieve the above object, according to one aspect of the present invention, there is provided a calibration apparatus for identifying static and dynamic loads of a radial bearing of a ship, comprising: the device comprises a wireless remote measuring device, a key phase signal acquisition device, a strain gauge, a loading device and a first pressure sensor;
the key phase signal acquisition device and the strain gauge are connected with the wireless transmission module on the corresponding shaft section, and the acquired data are sent to the wireless receiving module through the wireless transmission module to form a wireless data transmission system;
the loading device can select a mode of radial and axial loading or mixed loading on the test bearing, and select three working conditions of simulated unbalanced force, impact force and sinusoidal excitation;
the first pressure sensor is located between the test bearing and the base.
In some optional embodiments, the loading device is composed of a support module and a loading module, the loading module is arranged in the X direction and the Y direction of the support module to realize axial loading and radial loading, and the loading devices are arranged at the left end and the right end of the test bearing.
In some optional embodiments, the loading module is composed of a piezoelectric actuator, a transition device and a rolling bearing, the piezoelectric actuator and the transition device transmit a loading force through a loading rod plate, the rolling bearing is arranged on a shaft neck of the test shaft system, and a loading probe below the transition device is connected with the rolling bearing through a bolt.
In some optional embodiments, the transition device comprises a loading rod plate, a belleville spring and a second pressure sensor from top to bottom, wherein the upper portion of the loading rod plate is provided with a processed thread which is matched with a bottom screw hole of the piezoelectric actuator so as to transmit a loading force, the belleville spring is arranged between the loading rod plate and the second pressure sensor and used for buffering the phenomenon that the loading force fluctuates due to the change of the elongation of a rod of the piezoelectric actuator caused by the vibration of a rotating shaft, the second pressure sensor records the actual loading force of the loading device, a loading probe is arranged below the transition device, and a hole is formed in the middle of the transition device and used for connecting the rolling bearing.
In some optional embodiments, the key phase signal acquisition device comprises an eddy current sensor and an electroplated reflective strip, wherein the electroplated reflective strip is adhered to the rotating shaft, the eddy current sensor probe faces the position of the electroplated reflective strip, and the eddy current sensor is connected with the wireless transmission module.
In some optional embodiments, a plurality of cross sections are selected from the shaft section near the test bearing and are respectively arranged with strain gauges, each strain gauge is connected with the wireless transmitting module in a full-bridge arrangement mode, the strain gauges cannot be arranged on the same side of the test bearing, and the positions where the strain gauges are arranged and the electroplated reflective strips are on the same horizontal line.
In some optional embodiments, the number of signal access ports of the wireless transmitting module is greater than or equal to the sum of the number of the strain signals and the number of the key phase signals, and the wireless receiving module can synchronously receive the strain signals and the key phase signals transmitted by the plurality of wireless transmitting modules and is connected with the data analyzer.
According to another aspect of the present invention, there is provided a calibration method for a calibration apparatus based on the above identification of static and dynamic loads of a radial bearing of a ship, including:
(1) selecting a calibration test state, determining to perform static calibration or dynamic calibration on the radial bearing of the ship, and turning off the variable frequency motor if the static calibration is selected; if the dynamic calibration is selected, starting the variable frequency motor;
(2) selecting a simulation working condition, and determining to apply unbalanced force, impact force or sinusoidal excitation; if the simulated unbalanced force is selected, the loading device is not started, the rotating speed of the shafting is adjusted, and the shafting is caused to generate the unbalanced force through the rotation of the counterweight plate; if the simulation impact force or the sine excitation is selected, an impact electric signal or a sine electric signal is input into the loading device, and the piezoelectric actuator generates a corresponding loading force;
(3) the loading mode is selected, the loading device can provide X-direction loading, Y-direction loading and mixed loading, and one of the loading modes is selected for loading;
(4) the test shaft system is regarded as a variable cross-section continuous beam, the dead weight of each shaft section is regarded as uniformly distributed load, the high-elasticity coupling and the loading force are regarded as concentrated load, the initial value of the equivalent fulcrum correction coefficient of the test bearing is set to be 1, and the calculation formula of the equivalent fulcrum is as follows:
LFthe distance between the equivalent fulcrum of the bearing and the right end point of the bearing is shown, Z is the width of the bearing, and r is the correction coefficient of the equivalent fulcrum;
(5) after the pressure sensor, the key phase signal and the strain signal are stable, each group of section strain signals epsilon received by the wireless telemetering devicei(t) (i ═ 1,2,3, …) with a set of bond signals
Inputting a data analyzer, setting an initial value of a strain correction coefficient of a test section as 1, wherein a strain calculation formula is as follows: epsilon'i(t)＝εi(t)*α，εi(t) (i ═ 1,2,3, …) are strain signals for each set of cross sections, and α is a strain correction coefficient, ∈'i(t) is a strain correction value;
(6) the corrected strain signal is epsilon'i(t) (i ═ 1,2,3, …) and bond phase signal
Calculating the dynamic bending moment of the shafting;
(7) and establishing a calculation analysis model, and listing a stress balance equation and a moment balance equation for each unit, wherein the stress balance equation and the moment balance equation are listed. The unknown number is the section shearing force and the bearing support reaction force to be tested;
(8) recording the readings of the first pressure sensor of n sampling points within a certain time t1, carrying out error analysis on the readings and corresponding load identification values, and calculating whether the average error within the time t1 meets the set precision, wherein the judgment formula is as follows:
a is the set precision of the calibration test, FR(j) An indication of the first pressure sensor for each sample point during time period t1, f (j) an identification of the dynamic load for each sample point during time period t 1; if the calculation precision does not meet the actual requirement, returning to the step (4), adjusting the equivalent fulcrum correction coefficient and the strain correction coefficient for recalculation until the preset precision requirement is met;
(9) and after the precision requirement is met, recording the equivalent fulcrum correction coefficient and the strain correction coefficient under the working condition as a bearing load calibration result.
In some alternative embodiments, in step (6), the step (c) is performed by
The corrected strain signal epsilon'i(t) (i ═ 1,2,3, …) and bond phase signal
Calculating the dynamic bending moment of the shafting, wherein M is the bending moment of the section of the shaft section, E is the elastic modulus of the material of the shaft section,
is the journal bending section coefficient, d is the section diameter, IzIs the moment of inertia of the cross section of the shaft to the central axis.
In some alternative embodiments, in step (8), the step (c) is performed by
Judging whether the average error in t1 meets the set precision, wherein A is the set precision of the calibration test, FR(j) An indication of the first pressure sensor for each sample point during the time period t1, and f (j) a dynamic load identification value for each sample point during the time period t 1.
In general, compared with the prior art, the above technical solution contemplated by the present invention can achieve the following beneficial effects:
1. the calibration device for identifying static and dynamic loads of the ship radial bearing adopts a two-end loading scheme, simulates various loads borne by the ship radial bearing in an actual service period, designs a loading scheme combining a piezoelectric actuator, a transition device and a rolling bearing, and overcomes the defects of unstable loading force, larger vibration change along with a shaft system, low dynamic load frequency and the like of a traditional hydraulic loading system.
2. The ship radial bearing static and dynamic load calibration method simulates the impact force borne by a bearing by inputting impact electric signals, sine electric signals and the like to a loading device and simulates the unbalanced force borne by the bearing by the influence of a balance weight disc on a shafting. Compared with the traditional radial bearing load calibration method, the method can select two shafting states of static and dynamic states, select an axial and radial loading or mixed loading mode for the test bearing, select three working conditions of simulation unbalanced force, impact force and sine excitation, have abundant static and dynamic calibration conditions, and more truly simulate the external influence born by the bearing in the service period of the ship.
3. The ship radial bearing static and dynamic load calibration method sets equivalent fulcrum coefficients and strain correction coefficients, and compares the equivalent fulcrum coefficients and the strain correction coefficients with true values shown by a pressure sensor to perform precision analysis and promotion on calibration test results under given conditions so as to compensate errors caused by inaccurate positions of equivalent fulcrums of bearings.
In a word, the calibration device and the calibration method for identifying the static and dynamic loads of the ship radial bearing have the advantages of high precision, simplicity in operation, short calculation time, rich simulated working conditions and the like, and are particularly suitable for calibrating the method for identifying the load of the radial bearing of the ship propulsion shafting in the service period.
Drawings
Fig. 1 is a schematic structural diagram of a dynamic calibration device for a marine propulsion shafting bearing according to an embodiment of the present invention;
FIG. 2 is a block diagram of a loading module according to an embodiment of the present invention;
FIG. 3 is a schematic diagram of a loading apparatus according to an embodiment of the present invention;
FIG. 4 is a schematic view of a mechanical model of a shaft section of a test shafting according to an embodiment of the present invention;
FIG. 5 is a flowchart of a calibration method for static and dynamic load identification of a radial bearing of a ship provided by an embodiment of the invention;
in the figure: 1-a variable frequency motor; 2-coupling; 3-a first support bearing; 4-a base; 5-a first counterweight plate; 6-a second counterweight plate; 7-a second support bearing; 8-high elastic coupling; 9-a first loading device; 10-key phase signal acquisition means; 11-a first wireless transmitting device; 12-a first strain section; 13-a first pressure sensor; 14-testing the bearing; 15-a second strain cross-section; 16-third strain cross section; 17-a rotating shaft; 18-a second loading device; 19-a wireless receiving device; 20-a data analyzer; 21-a second wireless transmitting device; 22-a piezoelectric actuator; 23-a load bar plate; 24-a belleville spring; 25-a second pressure sensor; 26-rolling bearings; 27-bracket.
Detailed Description
In order to make the objects, technical solutions and advantages of the present invention more apparent, the present invention is described in further detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the invention and are not intended to limit the invention. In addition, the technical features involved in the embodiments of the present invention described below may be combined with each other as long as they do not conflict with each other.
In the present examples, "first", "second", etc. are used for distinguishing different objects, and are not necessarily used for describing a particular order or sequence.
Fig. 1 is a schematic structural diagram of a dynamic calibration device for a marine propulsion shafting according to an embodiment of the present invention, which is composed of a variable frequency motor 1, a first support bearing 3, a second support bearing 7, a rotating shaft 17, a first wireless transmitting device 11, a second wireless transmitting device 21, a wireless receiving device 19, a key phase signal collecting device 10, a coupling 2, a high-elasticity coupling 8, a first counterweight plate 5, a second counterweight plate 6, a strain gauge, a first loading device 9, a second loading device 18, a first pressure sensor 13, and a data analyzer 20.
The wireless receiving device 19, the first wireless transmitting device 11 and the second wireless transmitting device 21 form a wireless telemetering device, the first wireless transmitting device 11 is fixed on a shaft section on the left side of the test bearing 14 through an adhesive tape, the second wireless transmitting device 21 is fixed on a shaft section on the right side of the test bearing 14 through an adhesive tape, and the wireless receiving device 19 is connected with the data analyzer 20.
The key phase signal acquisition device 10 is composed of an eddy current sensor and an electroplating reflection strip, the eddy current sensor is fixed on the right side of the first loading device 9, the electroplating reflection strip is pasted on the surface of the rotating shaft 17 and is opposite to the probe of the eddy current sensor, and the eddy current sensor is connected with the first wireless transmitting device 11 through a lead. The first strain gauge on the first strain section 12, the second strain gauge on the second strain section 15 and the third strain gauge on the third strain section 16 are arranged on two sides of the test bearing 14 in a full-bridge connection mode, the first strain gauge is connected to the first wireless transmitting device 11, and the second strain gauge and the third strain gauge are connected to the second wireless transmitting device 21. The first pressure sensor 13 is mounted between the test bearing 14 and the base 4.
As shown in fig. 2, the loading module is composed of a piezoelectric actuator 22, a transition device and a rolling bearing 26, and simulates static and dynamic loads to which a ship shafting is subjected by inputting different forms of electric signals to the loading module. The loading module can select a mode of radial loading, axial loading or mixed loading to the test bearing, and selects three working conditions of simulation unbalanced force, impact force and sine excitation.
The transition device comprises a loading rod plate 23, a disc spring 24 and a second pressure sensor 25, wherein the upper portion of the loading rod plate 23 is provided with a processed thread which is matched with a bottom screw hole of the piezoelectric actuator 22 so as to transmit loading force, the disc spring 24 is arranged between the loading rod plate 23 and the second pressure sensor 25 and used for buffering the phenomenon that the loading force is unstable due to the fact that the extension amount of a piezoelectric actuator rod changes due to vibration of the rotating shaft 17, the second pressure sensor 25 records the actual loading force of the loading device, a loading probe is arranged below the transition device, and a round hole is formed in the middle of the transition device and used for being connected with a rolling bearing 26.
As shown in fig. 3, each loading device is composed of a bracket 27 and two loading modules in the x and y directions, and a circular hole is formed on the outer side of the rolling bearing 26 in the x and y directions, and is coupled with a loading probe below the loading module and connected with the loading probe through a bolt.
With reference to the above-described calibration device for identifying static and dynamic loads of a radial bearing of a ship, referring to fig. 1 to 3, a flow chart of the calibration method for identifying static and dynamic loads of a radial bearing of a ship is referring to fig. 5, and accuracy required by a test is satisfied by setting an equivalent fulcrum correction coefficient and a strain correction coefficient and adopting an iterative loop mode.
In the next example, the dynamic load identification calibration method of the radial sine excitation of the radial bearing of the ship under the condition of shafting rotation by the second loading device 18 comprises the following steps:
(1) setting a calibration test precision A, starting the variable frequency motor 1, inputting a sinusoidal electric signal to a radial loading module of the second loading device 18 after the rotating speed of a shaft system is stable, and reading a dynamic sinusoidal loading force T (t) through a second pressure sensor;
(2) the test shaft system is regarded as a variable cross-section continuous beam, the self weight of each shaft section is regarded as uniformly distributed load, the high-elastic coupling, loading force and the like are regarded as concentrated load, the initial value of the equivalent fulcrum correction coefficient of the test bearing is set to be 1, and the calculation formula of the equivalent fulcrum is as follows:
wherein L isFThe distance between the equivalent fulcrum of the bearing and the right end point of the bearing is; z is the bearing width in m; r is an equivalent fulcrum correction coefficient, and the default value is 1.
(3) After the sine excitation is stable, setting a strain correction coefficient alpha, and receiving three groups of strain section signals epsilon from the wireless telemetering devicei(t) (i ═ 1,2,3) with a set of bond phase signals
Inputting the strain section signals into a data analyzer, and calculating the corrected strain section signals, wherein the calculation formula is as follows:
ε'i(t)＝εi(t)*α
wherein: epsiloni(t) (i ═ 1,2,3) strain signals for three sets of sections; alpha is a strain correction coefficient; epsilon'i(t) a strain correction value.
(4) The corrected strain signal is epsilon'i(t) (i ═ 1,2,3) and bond phase signal
Calculating the dynamic bending moment of the shafting by the following formula:
wherein M is bending moment of the section of the shaft section with the unit of N.m, E is elastic modulus of the material of the shaft section with the unit of Pa,
is the bending section coefficient of the shaft neck, and is given by m3D is the cross-sectional diameter, IzIs the moment of inertia of the cross section of the shaft to the central axis.
(5) A computational analysis model is established, and referring to fig. 4, stress balance equations and moment balance equations are listed for two shaft sections obtained by cutting three groups of strain gauges, and 4 equations can be listed in total, as shown below. Wherein the unknown number is 3 section shearing forces Qi(i ═ 1,2,3) and 1 test bearing reaction force f (t), 4 unknowns of equation 4, can be uniquely solved.
Q1(t)-Q2(t)+F(t)＝q1L1
Q2(t)-Q3(t)＝q2L2
Wherein L isFMeasuring the distance between the cross-section to the right for the equivalent fulcrum position, Qi(t) (i ═ 1,2,3) represents each cross-sectional shear force, Mi(t) (i ═ 1,2,3) represents each section bending moment, F (t) represents a test bearing load identification value, and L representsi(i is 1,2) is the length of each shaft section, q isiAnd (i is 1 and 2) is an evenly distributed load corresponding to the dead weight of each shaft section.
(6) Recording the readings of the first pressure sensor 13 of n sampling points within a certain time t1, carrying out error analysis on the readings and corresponding load identification values, and calculating whether the average error within the time t1 meets the set precision, wherein the judgment formula is as follows:
wherein A is the set precision of the calibration test, FR(j) F (j) is the index of the first pressure sensor 13 at each sampling point in the time period t1, and f (j) is the dynamic load identification value at each sampling point in the time period t1, that is, f (j) is the jth sampling point in f (t) obtained in step (5).
(7) If the average error in the time t1 meets the discriminant, outputting the equivalent fulcrum coefficient and the strain correction coefficient as the calibration result, if the average error does not meet the discriminant, returning to the step (2), adjusting the equivalent fulcrum coefficient and the strain correction coefficient, recalculating until the accuracy requirement is met, and outputting the equivalent fulcrum coefficient and the strain correction coefficient as the calibration result under the working condition.
It should be noted that, according to the implementation requirement, each step/component described in the present application can be divided into more steps/components, and two or more steps/components or partial operations of the steps/components can be combined into new steps/components to achieve the purpose of the present invention.
It will be understood by those skilled in the art that the foregoing is only a preferred embodiment of the present invention, and is not intended to limit the invention, and that any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the scope of the present invention.
Claims (9)
1. A calibration method of a calibration device based on ship radial bearing static and dynamic load identification is provided, wherein the calibration device comprises: the device comprises a wireless remote measuring device, a key phase signal acquisition device, a strain gauge, a loading device and a first pressure sensor; the key phase signal acquisition device and the strain gauge are connected with the wireless transmission module on the corresponding shaft section, and the acquired data are sent to the wireless receiving module through the wireless transmission module to form a wireless data transmission system; the loading device can select a mode of radial and axial loading or mixed loading on the test bearing, and select three working conditions of simulated unbalanced force, impact force and sinusoidal excitation; the first pressure sensor is positioned between the test bearing and the base, and the calibration method is characterized by comprising the following steps:
(1) selecting a calibration test state, determining to perform static calibration or dynamic calibration on the radial bearing of the ship, and turning off the variable frequency motor if the static calibration is selected; if the dynamic calibration is selected, starting the variable frequency motor;
(2) selecting a simulation working condition, and determining to apply unbalanced force, impact force or sine excitation; if the simulated unbalanced force is selected, the loading device is not started, the rotating speed of the shafting is adjusted, and the shafting is caused to generate the unbalanced force through the rotation of the counterweight plate; if the simulation impact force or the sine excitation is selected, an impact electric signal or a sine electric signal is input into the loading device, and the piezoelectric actuator generates a corresponding loading force;
(3) the loading mode is selected, the loading device can provide X-direction loading, Y-direction loading and mixed loading, and one of the loading modes is selected for loading;
(4) the test shaft system is regarded as a variable cross-section continuous beam, the dead weight of each shaft section is regarded as uniformly distributed load, the high-elasticity coupling and the loading force are regarded as concentrated load, the initial value of the equivalent fulcrum correction coefficient of the test bearing is set to be 1, and the calculation formula of the equivalent fulcrum is as follows:
LFthe distance between the equivalent fulcrum of the bearing and the right end point of the bearing is shown, Z is the width of the bearing, and r is the correction coefficient of the equivalent fulcrum;
(5) after the pressure sensor, the key phase signal and the strain signal are stable, each group of section strain signals epsilon received by the wireless telemetering devicei(t) (i ═ 1,2,3, …) with a set of bond signals
Inputting a data analyzer, setting an initial value of a strain correction coefficient of a test section as 1, wherein a strain calculation formula is as follows: epsilon'i(t)＝εi(t)*α，εi(t) (i ═ 1,2,3, …) are strain signals for each set of cross sections, and α is a strain correction coefficient, ∈'i(t) is a strain correction value;
(6) the corrected strain signal is epsilon'i(t) (i ═ 1,2,3, …) and bond phase signal
Calculating the dynamic bending moment of the shafting;
(7) establishing a computational analysis model, and listing a stress balance equation and a moment balance equation for each unit, wherein the unknown number is a section shearing force and a test bearing support reaction force;
(8) recording the readings of the first pressure sensor of n sampling points within a certain time t1, carrying out error analysis on the readings and corresponding load identification values, and calculating whether the average error within the time t1 meets the set precision, wherein the judgment formula is as follows:
a is the set precision of the calibration test, FR(j) An indication of the first pressure sensor for each sample point during time period t1, f (j) an identification of the dynamic load for each sample point during time period t 1; if the calculation precision does not meet the actual requirement, returning to the step (4), adjusting the equivalent fulcrum correction coefficient and the strain correction coefficient for recalculation until the preset precision requirement is met;
(9) and after the precision requirement is met, recording the equivalent fulcrum correction coefficient and the strain correction coefficient under the working condition as a bearing load calibration result.
2. The calibration method according to claim 1, wherein the loading device comprises a support module and a loading module, the loading module is arranged in the X direction and the Y direction of the support module to realize axial loading and radial loading, and the loading devices are respectively arranged at the left end and the right end of the test bearing.
3. The calibration method according to claim 2, wherein the loading module comprises a piezoelectric actuator, a transition device and a rolling bearing, the piezoelectric actuator and the transition device transmit a loading force through a loading rod plate, the rolling bearing is arranged on a shaft neck of a test shaft system, and a loading probe below the transition device is connected with the rolling bearing through a bolt.
4. The calibration method according to claim 3, wherein the transition device comprises a loading rod plate, a belleville spring and a second pressure sensor from top to bottom, wherein the upper portion of the loading rod plate is provided with a processed thread which is matched with a bottom screw hole of the piezoelectric actuator so as to transmit the loading force, the belleville spring is arranged between the loading rod plate and the second pressure sensor and used for buffering the phenomenon that the loading force fluctuates due to the change of the elongation of the piezoelectric actuator rod caused by the vibration of the rotating shaft, the second pressure sensor records the actual loading force of the loading device, a loading probe is arranged below the transition device, and a hole is formed in the middle of the transition device and used for connecting a rolling bearing.
5. The calibration method according to any one of claims 1 to 4, wherein the key phase signal acquisition device comprises an eddy current sensor and an electroplated reflective strip, wherein the electroplated reflective strip is adhered to the rotating shaft, the probe of the eddy current sensor faces the position of the electroplated reflective strip, and the eddy current sensor is connected with the wireless transmission module.
6. The calibration method according to claim 5, wherein a plurality of cross sections are selected at the shaft section near the test bearing and are respectively arranged with strain gauges, each strain gauge is connected with the wireless transmission module in a full-bridge arrangement mode, the strain gauges cannot be arranged at the same side of the test bearing, and the positions where the strain gauges are arranged should be on the same horizontal line with the electroplated reflective strips.
7. The calibration method according to claim 6, wherein the number of signal access ports of the wireless transmission module is greater than or equal to the sum of the number of the strain signals and the number of the key phase signals, and the wireless reception module can synchronously receive the strain signals and the key phase signals transmitted by the plurality of wireless transmission modules and is connected with the data analyzer.
8. Calibration method according to claim 1, characterized in thatCharacterized in that, in step (6), the reaction is carried out by
The corrected strain signal epsilon'i(t) (i ═ 1,2,3, …) and key phase signal
Calculating the dynamic bending moment of the shafting, wherein M is the bending moment of the section of the shaft section, E is the elastic modulus of the material of the shaft section,
is the journal bending section coefficient, d is the section diameter, IzIs the moment of inertia of the cross section of the shaft to the central axis.
9. Calibration method according to claim 8, characterized in that in step (8) the method is performed by
Judging whether the average error in t1 meets the set precision, wherein A is the set precision of the calibration test, FR(j) An indication of the first pressure sensor for each sample point during the time period t1, and f (j) a dynamic load identification value for each sample point during the time period t 1.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010928382.XA CN112033672B (en) | 2020-09-07 | 2020-09-07 | Calibration device and calibration method for static and dynamic load identification of ship radial bearing |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202010928382.XA CN112033672B (en) | 2020-09-07 | 2020-09-07 | Calibration device and calibration method for static and dynamic load identification of ship radial bearing |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN112033672A CN112033672A (en) | 2020-12-04 |
| CN112033672B true CN112033672B (en) | 2022-05-06 |
Family
ID=73584162
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202010928382.XA Active CN112033672B (en) | 2020-09-07 | 2020-09-07 | Calibration device and calibration method for static and dynamic load identification of ship radial bearing |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN112033672B (en) |
Families Citing this family (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112393905B (en) * | 2020-12-14 | 2022-09-20 | 大连工业大学 | Rolling bearing tester with external impact excitation |
| CN112697367A (en) * | 2020-12-23 | 2021-04-23 | 武汉理工大学 | Boats and ships propulsion shafting longitudinal and transverse coupling vibration experiment platform |
| CN113155454B (en) * | 2021-02-03 | 2022-04-22 | 浙江万向精工有限公司 | Strain calibration method of dynamic test bed of hub bearing |
| CN114486057B (en) * | 2021-12-30 | 2024-05-31 | 西安航天计量测试研究所 | Non-contact pressure measurement method and system based on strain and temperature sensors |
| CN114486144B (en) * | 2022-01-10 | 2024-06-14 | 武汉船用电力推进装置研究所（中国船舶重工集团公司第七一二研究所） | Radial impact load simulation test device of nacelle propeller propulsion shafting |
| CN115111262A (en) * | 2022-07-04 | 2022-09-27 | 中国舰船研究设计中心 | Ship long shafting anti-impact protection device and design method thereof |
| CN116067553B (en) * | 2022-12-16 | 2024-05-10 | 上海核工程研究设计院股份有限公司 | Load measurement method for section steel of nuclear power plant |
| CN115808310B (en) * | 2023-02-09 | 2023-05-12 | 哈尔滨科锐同创机模制造有限公司 | Test parameter calibration method and system applied to bearing test |
| CN116929764B (en) * | 2023-07-31 | 2024-05-17 | 上海大学 | Measuring equipment for dynamic oil film thickness and pressure of wind power sliding bearing |
Citations (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6199425B1 (en) * | 1999-07-28 | 2001-03-13 | International Business Machines Corporation | Apparatus and method for testing thrust bearings |
| BRPI0606311A (en) * | 2006-12-29 | 2008-08-19 | Comissao Nac Energia Nuclear | design and construction process of an instrumented fatigue testing machine for the determination of material fatigue properties in a controlled environment capable of simultaneously testing 10 specimens with individual loading and environments |
| DE102009016161A1 (en) * | 2009-04-03 | 2010-10-07 | Schaeffler Technologies Gmbh & Co. Kg | Device for noise-testing of ball bearing in flexible assembly system in vehicle, has load unit for transmitting load to radial bearing, such that real load of radial bearing is simulated using operating conditions |
| CN102269654A (en) * | 2011-05-10 | 2011-12-07 | 重庆大学 | Water lubricated bearing and transmission system comprehensive performance testing platform |
| CN202216820U (en) * | 2011-07-19 | 2012-05-09 | 华中科技大学 | Simulation test stand of longitudinal vibration of marine propulsion shafting |
| CN102650556A (en) * | 2012-05-14 | 2012-08-29 | 云南电力试验研究院（集团）有限公司电力研究院 | Bearing load identification method based on strain signals of three cross sections of rotating shaft |
| CN102928222A (en) * | 2012-09-29 | 2013-02-13 | 广东电网公司电力科学研究院 | Method for testing and identifying dynamic characteristic coefficients of sliding bearing |
| CN102980765A (en) * | 2012-12-12 | 2013-03-20 | 武汉理工大学 | Comprehensive test platform for marine shafting |
| WO2014123883A1 (en) * | 2013-02-05 | 2014-08-14 | One-G, Llc | Aircraft simulator |
| CN104792532A (en) * | 2015-04-28 | 2015-07-22 | 中国船舶重工集团公司第七一一研究所 | Marine thrust bearing equipment test apparatus |
| CN106996871A (en) * | 2017-04-07 | 2017-08-01 | 中国船舶科学研究中心（中国船舶重工集团公司第七0二研究所） | Real yardstick marine propulsion shafting vibration transmissibility experimental rig |
| CN109520735A (en) * | 2018-10-26 | 2019-03-26 | 中国第汽车股份有限公司 | Loading ability of bearing loses test macro |
| CN110954427A (en) * | 2019-12-18 | 2020-04-03 | 武汉理工大学 | Multifunctional miniature precision bearing experiment platform |
-
2020
- 2020-09-07 CN CN202010928382.XA patent/CN112033672B/en active Active
Patent Citations (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6199425B1 (en) * | 1999-07-28 | 2001-03-13 | International Business Machines Corporation | Apparatus and method for testing thrust bearings |
| BRPI0606311A (en) * | 2006-12-29 | 2008-08-19 | Comissao Nac Energia Nuclear | design and construction process of an instrumented fatigue testing machine for the determination of material fatigue properties in a controlled environment capable of simultaneously testing 10 specimens with individual loading and environments |
| DE102009016161A1 (en) * | 2009-04-03 | 2010-10-07 | Schaeffler Technologies Gmbh & Co. Kg | Device for noise-testing of ball bearing in flexible assembly system in vehicle, has load unit for transmitting load to radial bearing, such that real load of radial bearing is simulated using operating conditions |
| CN102269654A (en) * | 2011-05-10 | 2011-12-07 | 重庆大学 | Water lubricated bearing and transmission system comprehensive performance testing platform |
| CN202216820U (en) * | 2011-07-19 | 2012-05-09 | 华中科技大学 | Simulation test stand of longitudinal vibration of marine propulsion shafting |
| CN102650556A (en) * | 2012-05-14 | 2012-08-29 | 云南电力试验研究院（集团）有限公司电力研究院 | Bearing load identification method based on strain signals of three cross sections of rotating shaft |
| CN102928222A (en) * | 2012-09-29 | 2013-02-13 | 广东电网公司电力科学研究院 | Method for testing and identifying dynamic characteristic coefficients of sliding bearing |
| CN102980765A (en) * | 2012-12-12 | 2013-03-20 | 武汉理工大学 | Comprehensive test platform for marine shafting |
| WO2014123883A1 (en) * | 2013-02-05 | 2014-08-14 | One-G, Llc | Aircraft simulator |
| CN104792532A (en) * | 2015-04-28 | 2015-07-22 | 中国船舶重工集团公司第七一一研究所 | Marine thrust bearing equipment test apparatus |
| CN106996871A (en) * | 2017-04-07 | 2017-08-01 | 中国船舶科学研究中心（中国船舶重工集团公司第七0二研究所） | Real yardstick marine propulsion shafting vibration transmissibility experimental rig |
| CN109520735A (en) * | 2018-10-26 | 2019-03-26 | 中国第汽车股份有限公司 | Loading ability of bearing loses test macro |
| CN110954427A (en) * | 2019-12-18 | 2020-04-03 | 武汉理工大学 | Multifunctional miniature precision bearing experiment platform |
Non-Patent Citations (2)
| Title |
|---|
| Vibration analysis of marine propulsion shafting by the coupled finite element method;Huang, Qianwen等;《JOURNAL OF VIBROENGINEERING》;20151130;第17卷(第7期);第3392-3403页 * |
| 基于熵权模糊综合评价法的水润滑尾轴承性能评估;欧阳武 等;《中国机械工程》;20200630;第31卷(第12期);第1407-1414页 * |
Also Published As
| Publication number | Publication date |
|---|---|
| CN112033672A (en) | 2020-12-04 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN112033672B (en) | Calibration device and calibration method for static and dynamic load identification of ship radial bearing | |
| CN101839798B (en) | Device for hypersonic pitching dynamic test | |
| CN102095574B (en) | Joint surface dynamic characteristic parameter testing device of rolling guide rail and testing method thereof | |
| CN101988879B (en) | Loading detection method for sulphide stress corrosion uniaxial tensile test and monitoring system thereof | |
| CN102323058B (en) | Device and method for identifying bearing load of turbo generator set based on strain signal of rotating shaft | |
| CN112100765A (en) | High-low cycle composite fatigue test piece of turbine disc cold extrusion reinforced hole structure and design method | |
| CN110501107B (en) | Spacecraft rotation load dynamic balance measurement method based on six-dimensional force tester | |
| CN103837275A (en) | Dynamic bending moment test system for ship shafting | |
| CN108760545B (en) | Mean load loading error compensation method for resonant fatigue testing machine | |
| CN112816001A (en) | Jacking process-based synchronous testing method for load displacement of bearings of multiple support shaft systems | |
| CN111859679A (en) | Wind turbine generator test load obtaining method, simulation load comparing method and simulation load comparing device | |
| CN115855477A (en) | Device and method for testing robot joint performance | |
| Rhew | NASA LaRC Strain Gage Balance Design Concepts | |
| CN111473859A (en) | Method for making vibration limit value of whole machine | |
| CN103822769A (en) | Three-direction force-measuring loop | |
| CN107748112B (en) | Device and method for measuring circumferential angle and circumferential displacement | |
| CN208860596U (en) | Aluminum enclosure bearing block Thermal-mechanical Coupling strain measurement system | |
| CN114689265B (en) | Dynamic calibration method for structural bending moment in aeroelastic wind tunnel test of elastic wing | |
| CN110441054A (en) | Rotating machinery shafting misaligns fault condition detection method under shaft coupling connection status | |
| CN115200859B (en) | Torque meter and use method thereof | |
| KR102608312B1 (en) | Thrust and torque measurement equipment using data post-processing for ship model tests | |
| CN114184352B (en) | Nacelle power meter model test balance device and use method | |
| CN101165461A (en) | Speed/acceleration vibration system checking instrument | |
| CN116296237B (en) | Vertical wind load test method for large carrier rocket in low-speed wind tunnel | |
| CN115636063A (en) | High-precision real-time identification method and device for thrust of ship propeller shaft |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |